Pump body assembly and fluid machine

Abstract

The invention provides a pump body assembly and a fluid machine. The pump body assembly comprises a crankshaft provided with two eccentric parts in the axial direction of the crankshaft; the crankshaft and the cylinder sleeve are eccentrically arranged, and the eccentric distance is fixed; the piston assembly comprises a piston sleeve and a piston, the piston sleeve is rotatably arranged in the cylinder sleeve, the piston sleeve is provided with two limiting channels which are sequentially arranged in the axial direction of the crankshaft, the limiting channels extend in the radial direction of the piston sleeve, and an oil storage groove is formed in the peripheral face of the piston sleeve; the pistons are provided with through holes, the number of the pistons is two, the two eccentric parts correspondingly extend into the two through holes, the two pistons are correspondingly arranged in the two limiting channels in a sliding mode and form two variable volume cavities respectively, and the crankshaft rotates to drive the pistons to slide in the limiting channels in a reciprocating mode and meanwhile interact with the piston sleeve, so that the piston sleeve and the pistons rotate in the cylinder sleeve; the number of the flanges is two, and the two flanges are arranged at the two axial ends of the cylinder sleeve respectively. The problem that in the prior art, the operation reliability of a pump body assembly is poor is solved.

Description

Technical Field

[0001] The present invention relates to the technical field of heat exchange equipment, and in particular to a pump body component and a fluid machinery. Background Art

[0002] With the development of society, the power consumption of data centers is increasing year by year, resulting in huge power consumption. Computer room air conditioning is an important part of the data center, accounting for 40% of the power consumption of the data center. The application of its energy-saving technology is of great significance.

[0003] Computer room air conditioners are devices used to cool the electrical components of data centers. They need to be cooled continuously all year round to ensure that the indoor temperature can be maintained within a certain range. Most of the existing computer room air conditioners use compression refrigeration technology, and rely on compression refrigeration systems for cooling in both summer and winter. When the ambient temperature is high, the existing compression refrigeration technology can meet the performance and energy efficiency requirements; when the outdoor ambient temperature is significantly lower than the indoor temperature, the most economical and energy-saving refrigeration method is to use the low temperature outdoors to cool the indoor temperature. At this time, a liquid pump can be used instead of a compressor to drive the refrigerant to run in the system, which has higher energy efficiency than conventional air conditioning systems. In the industry, this system that uses a pump to drive the refrigerant is called a fluorine pump system; the pump that drives the refrigerant is called a fluorine pump.

[0004] However, when the existing fluorine pump is in operation, the piston assembly rotates at high speed in the cylinder sleeve, and the surfaces of the parts rub against each other, generating friction power consumption, reducing the energy efficiency of the fluorine pump, and at the same time reducing the service life of the fluorine pump, greatly affecting the performance and operational reliability of the fluorine pump.

[0005] As can be seen from the above, the prior art has the problem of poor operating reliability of the pump assembly. Summary of the invention

[0006] The main purpose of the present invention is to provide a pump body assembly and a fluid machine to solve the problem of poor operating reliability of the pump body assembly in the prior art.

[0007] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, a pump body assembly is provided, comprising: a crankshaft, wherein the crankshaft is provided with two eccentric parts along its axial direction; a cylinder sleeve, wherein the crankshaft and the cylinder sleeve are eccentrically arranged and the eccentric distance is fixed; a piston assembly, wherein the piston sleeve is rotatably arranged in the cylinder sleeve, the piston sleeve has two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, the limiting channels extend along the radial direction of the piston sleeve, and the outer peripheral surface of the piston sleeve is provided with an oil storage groove for storing cooling oil; the piston has a through hole, and there are two pistons, and the two eccentric parts extend into the two pistons correspondingly. In the two through holes, two pistons are correspondingly slidably arranged in the two limiting channels and respectively form two variable volume chambers, the two variable volume chambers are respectively located in the sliding directions of the two pistons, the crankshaft rotates to drive the piston to slide back and forth in the limiting channels while interacting with the piston sleeve to make the piston sleeve and the piston rotate in the cylinder sleeve; flange, there are two flanges, and the two flanges are respectively arranged at the axial ends of the cylinder sleeve; the cylinder sleeve is provided with a liquid inlet channel and a liquid discharge channel, the liquid inlet channel is connected with the variable volume chamber and transports refrigerant to the variable volume chamber, the liquid discharge channel is connected with the variable volume chamber and the refrigerant in the variable volume chamber is discharged through the liquid discharge channel.

[0008] Furthermore, the cylinder sleeve has a central portion, which divides the liquid inlet channel into two sub-channels, and the two sub-channels are respectively connected to the two variable volume chambers. The sealing height H1 between the piston sleeve and the central portion, the length L1 of the oil storage tank, and the height H3 of the central portion satisfy: 0.1mm≤H1≤H3-L1-0.1mm.

[0009] Furthermore, the overlapping height H2 between the oil storage tank and the drainage channel and the width H4 of the drainage channel satisfy: 0.1 mm ≤ H2 ≤ 0.8×H4.

[0010] Furthermore, the cylinder liner has a central portion, which divides the liquid inlet channel into two sub-channels, the two sub-channels are respectively connected to the two variable volume chambers, and the distance H5 between the oil storage tank and the corresponding limit channel and the distance H6 between the two limit channels satisfy: 0.1mm≤H5≤H6.

[0011] Furthermore, the width B of the oil storage tank satisfies: 0.5 mm ≤ B ≤ 5 mm.

[0012] Furthermore, the depth H7 of the oil storage groove, the diameter D1 of the piston sleeve, and the width L2 of the limiting channel satisfy the following relationship: 0.2 mm ≤ H7 ≤ 0.1*(D1-L2).

[0013] Further, when the oil storage groove is a rotary cut trapezoidal groove or a trapezoidal groove, the bottom vertex angle β of the oil storage groove satisfies: 95°<β<175°.

[0014] Furthermore, the oil storage tank is arranged corresponding to the radial opening of the limiting channel.

[0015] Furthermore, there are one or more oil storage grooves. When there are multiple oil storage grooves, the multiple oil storage grooves are arranged at intervals along the circumference of the piston sleeve.

[0016] Furthermore, the piston sleeve is provided with a central hole for avoiding the crankshaft and oil holes extending in the radial direction, and the oil holes are respectively connected with the central hole and the oil storage tank.

[0017] Furthermore, the periphery of the oil hole is located within the periphery of the bottom of the oil storage tank.

[0018] Furthermore, the oil storage tank is any one of a rotary cut trapezoidal groove, a sunken straight groove, a trapezoidal groove or a circular sunken groove.

[0019] Furthermore, the two eccentric portions are arranged at an angle of 180°.

[0020] According to another aspect of the present invention, a fluid machine is provided, comprising the above-mentioned pump body assembly.

[0021] Furthermore, the fluid machinery is a fluorine pump.

[0022] According to the technical solution of the present invention, a pump body assembly includes a crankshaft, a cylinder sleeve, a piston assembly and a flange. The crankshaft is provided with two eccentric parts along its axial direction. The crankshaft and the cylinder sleeve are eccentrically arranged and the eccentric distance is fixed. The piston assembly includes a piston sleeve and a piston, wherein the piston sleeve is rotatably arranged in the cylinder sleeve, the piston sleeve has two limiting channels, the two limiting channels are sequentially arranged along the axial direction of the crankshaft, the limiting channels extend along the radial direction of the piston sleeve, an oil storage groove is provided on the outer peripheral surface of the piston sleeve for storing cooling oil, the piston has a through hole, there are two pistons, the two eccentric parts extend into the two through holes of the two pistons correspondingly, the two pistons are correspondingly slidably arranged in the two limiting channels and respectively form two variable volume chambers, the two variable volume chambers are respectively located in the sliding directions of the two pistons, and the crankshaft rotates to The piston is driven to slide back and forth in the limiting channel while interacting with the piston sleeve to make the piston sleeve and the piston rotate in the cylinder sleeve. There are two flanges, which are respectively arranged at the axial ends of the cylinder sleeve. An inlet channel and a discharge channel are arranged on the cylinder sleeve. The inlet channel is connected with the variable volume chamber and transports refrigerant to the variable volume chamber. The discharge channel is connected with the variable volume chamber and discharges the refrigerant in the variable volume chamber through the discharge channel. In this way, by adding an oil storage groove on the outer circumferential surface of the piston sleeve, the lubrication between the contact surface of the piston sleeve and the cylinder sleeve can be improved, the wear of the inner circle of the cylinder sleeve and the outer circle of the piston sleeve can be reduced, and the friction power consumption can be greatly reduced, thereby ensuring the energy efficiency of the pump body assembly, and then improving the operating reliability of the pump body assembly, and solving the problem of poor operating reliability of the pump body assembly in the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0024] Figure 1 An exploded view of a pump assembly in a specific embodiment of the present invention is shown;

[0025] Figure 2 A cross-sectional view of a pump assembly in a specific embodiment of the present invention is shown;

[0026] Figure 3 A cross-sectional view at an angle of a cylinder sleeve in a specific embodiment of the present invention is shown;

[0027] Figure 4 A cross-sectional view at another angle of a cylinder sleeve in a specific embodiment of the present invention is shown;

[0028] Figure 5 Shows Figure 4 A partial enlarged view of the middle A;

[0029] Figure 6 Shows Figure 4 A partial enlarged view of point B in the middle;

[0030] Figure 7 A schematic structural diagram showing an angle of a piston sleeve in a specific embodiment of the present invention;

[0031] Figure 8 A schematic structural diagram showing another angle of a piston sleeve in a specific embodiment of the present invention;

[0032] Fig. 9 A schematic structural diagram showing an angle of a piston sleeve in another specific embodiment of the present invention;

[0033] Fig.10 A schematic structural diagram showing another angle of a piston sleeve in another specific embodiment of the present invention;

[0034] Fig.11 A cross-sectional view of a piston sleeve in another specific embodiment of the present invention is shown;

[0035] Fig.12 A cross-sectional view of an oil storage tank in a specific embodiment of the present invention is shown.

[0036] The above drawings include the following reference numerals:

[0037] 10. Crankshaft; 11. Eccentric part; 20. Cylinder liner; 21. Liquid inlet channel; 22. Liquid discharge channel; 23. Center part; 30. Piston assembly; 31. Piston sleeve; 311. Limiting channel; 312. Variable volume chamber; 313. Oil storage tank; 314. Center hole; 315. Oil hole; 32. Piston; 321. Through hole; 322. Extrusion surface; 323. Pressure relief guide groove; 40. Flange. DETAILED DESCRIPTION

[0038] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0039] In order to solve the problem of poor operating reliability of the pump assembly in the prior art, the present invention provides a pump assembly and a fluid machine, wherein the fluid machine includes the pump assembly.

[0040] like Figures 1 to 3 As shown, the pump body assembly includes a crankshaft 10, a cylinder sleeve 20, a piston assembly 30 and a flange 40. The crankshaft 10 is provided with two eccentric parts 11 along its axial direction. The crankshaft 10 and the cylinder sleeve 20 are eccentrically arranged and the eccentric distance is fixed. The piston assembly 30 includes a piston sleeve 31 and a piston 32, wherein the piston sleeve 31 is rotatably arranged in the cylinder sleeve 20, and the piston sleeve 31 has two limiting channels 311, which are sequentially arranged along the axial direction of the crankshaft 10, and the limiting channels 311 extend along the radial direction of the piston sleeve 31, and the outer peripheral surface of the piston sleeve 31 is provided with an oil storage groove 313 for storing cooling oil. The piston 32 has a through hole 321. There are two pistons 32. The two eccentric parts 11 extend into the two through holes 321 of the two pistons 32. The two pistons 32 are slidably arranged in the two limiting channels 311 and form two variable volume chambers 312 respectively. The two variable volume chambers 312 are respectively located in the sliding direction of the two pistons 32. The crankshaft 10 rotates to drive the piston 32 to slide back and forth in the limiting channel 311 and interact with the piston sleeve 31, so that the piston sleeve 31 and the piston 32 rotate in the cylinder sleeve 20. There are two flanges 40, and the two flanges 40 are respectively arranged at the axial ends of the cylinder sleeve 20. The cylinder sleeve 20 is provided with a liquid inlet channel 21 and a liquid discharge channel 22. The liquid inlet channel 21 is connected with the variable volume chamber 312 and transports the refrigerant into the variable volume chamber 312. The liquid discharge channel 22 is connected with the variable volume chamber 312 and the refrigerant in the variable volume chamber 312 is discharged from the liquid discharge channel 22.

[0041] By adding an oil storage groove 313 to the outer circumferential surface of the piston sleeve 31, the lubrication between the contact surface of the piston sleeve 31 and the cylinder sleeve 20 can be improved, the wear of the inner circle of the cylinder sleeve 20 and the outer circle of the piston sleeve 31 can be reduced, and the friction power consumption is greatly reduced, thereby ensuring the energy efficiency of the pump body assembly and further improving the operating reliability of the pump body assembly.

[0042] In this embodiment, when the pump assembly is in operation, a single variable volume chamber 312 is composed of a piston groove surface, a piston head surface, a flange end surface, and an inner circular surface of a cylinder sleeve.

[0043] In this embodiment, the inlet channel 21 and the discharge channel 22 are arranged 180 degrees opposite to each other in the circumferential direction of the pump body assembly, that is, the inlet channel 21 and the discharge channel 22 are arranged opposite to each other on the cylinder sleeve 20. There are two discharge channels 22, which are arranged at intervals up and down and are connected to the two variable volume chambers 312 respectively.

[0044] In this embodiment, the two eccentric portions 11 are arranged at an angle of 180°.

[0045] In this embodiment, there is a phase difference of a first angle between the two eccentric parts 11, the eccentricity of the two eccentric parts 11 is equal, and there is a limit difference of a second angle between the extension directions of the two limit channels 311, wherein the first angle is twice the second angle. In this way, when one of the two pistons 32 is at the dead point position, that is, the driving torque of the eccentric part 11 corresponding to the piston 32 at the dead point position is 0, and the piston 32 at the dead point position cannot continue to rotate. At this time, the driving torque of the other eccentric part 11 of the two eccentric parts 11 driving the corresponding piston 32 is the maximum value, ensuring that the eccentric part 11 with the maximum driving torque can normally drive the corresponding piston 32 to rotate, thereby driving the piston sleeve 31 to rotate through the piston 32, and then driving the piston 32 at the dead point position to continue to rotate through the piston sleeve 31, thereby realizing the stable operation of the rotary cylinder pump.

[0046] like Figure 1 As shown, the limiting channel 311 has a set of first sliding surfaces that are oppositely arranged and in sliding contact with the piston 32, the piston 32 has a second sliding surface that cooperates with the first sliding surface, the piston 32 has an extrusion surface 322 facing the end of the limiting channel 311, the extrusion surface 322 serves as the head of the piston 32, the two second sliding surfaces are connected by the extrusion surface 322, and the extrusion surface 322 faces the variable volume chamber 312. Furthermore, a pressure relief guide groove 323 is also provided on the extrusion surface 322.

[0047] In this embodiment, when the pump assembly is running, the crankshaft 10 rotates around the axis of the crankshaft 10; the piston sleeve 31 revolves around the axis of the crankshaft 10, and the axis of the crankshaft 10 is eccentrically arranged with the axis of the piston sleeve 31 and the eccentric distance is fixed; the first piston 32 performs a circular motion with the axis of the crankshaft 10 as the center, and the distance between the center of the first piston 32 and the axis of the crankshaft 10 is equal to the eccentricity of the first eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentric distance between the axis of the crankshaft 10 and the axis of the piston sleeve 31, the crankshaft 10 rotates to drive the first piston 32 to perform a circular motion, and The first piston 32 interacts with the piston sleeve 31 and slides back and forth in the limiting channel 311 of the piston sleeve 31; the second piston 32 makes a circular motion with the axis of the crankshaft 10 as the center, and the distance between the center of the second piston 32 and the axis of the crankshaft 10 is equal to the eccentricity of the second eccentric part 11 corresponding to the crankshaft 10, and the eccentricity is equal to the eccentric distance between the axis of the crankshaft 10 and the axis of the piston sleeve 31. The crankshaft 10 rotates to drive the second piston 32 to make a circular motion, and the second piston 32 interacts with the piston sleeve 31 and slides back and forth in the limiting channel 311 of the piston sleeve 31.

[0048] The pump body assembly in this embodiment constitutes a cross slider mechanism, and the operating method adopts the principle of the cross slider mechanism.

[0049] In this embodiment, the running track of the piston 32 is a circle, and the circle takes the axis of the crankshaft 10 as the center and the line connecting the axis of the crankshaft 10 and the axis of the piston sleeve 31 as the radius.

[0050] In this embodiment, the oil storage tank 313 is disposed corresponding to the radial opening of the limiting channel 311. Figures 7 to 10 As shown, the oil storage groove 313 is located above or below the radial opening of the limiting channel 311 .

[0051] In this embodiment, there are one or more oil storage grooves 313. When there are multiple oil storage grooves 313, the multiple oil storage grooves 313 are arranged at intervals along the circumference of the piston sleeve 31. Furthermore, the multiple oil storage grooves 313 are arranged at equal intervals along the circumference of the piston sleeve 31.

[0052] In a specific embodiment, there are four oil storage grooves 313, which are respectively located above or below the radial openings at both ends of the upper and lower limiting channels 311. In other words, the four oil storage grooves 313 are opposite to each other and are arranged with a phase difference of 90° along the circumference of the piston sleeve 31.

[0053] like Figures 4 to 5 As shown, the cylinder sleeve 20 has a central portion 23, and the central portion 23 divides the liquid inlet channel 21 into two sub-channels, and the two sub-channels are respectively connected to the two variable volume chambers 312. Figures 4 to 5 as well as Figure 8As shown, the sealing height H1 between the piston sleeve 31 and the center portion 23, the length L1 of the oil storage groove 313, and the height H3 of the center portion 23 satisfy: 0.1mm≤H1≤H3-L1-0.1mm. It can be understood that the sealing height between the piston sleeve 31 and the center portion 23 is the height of the outer side of the oil storage groove 313 of the piston sleeve 31 abutting against the center portion 23. Through the above arrangement, it can be ensured that the oil storage groove 313 is not connected to the liquid inlet channel 21 when passing through the liquid inlet position, preventing the oil storage groove 313 from leaking and affecting the heat exchange and performance of the pump body assembly.

[0054] Further, such as Figure 4 and Figure 6 As shown, the overlap height H2 of the oil storage tank 313 and the discharge channel 22 and the width H4 of the discharge channel 22 satisfy: 0.1mm≤H2≤0.8×H4. Through the above arrangement, it is possible to ensure that the oil storage tank 313 is connected to the discharge channel 22 to store the refrigeration oil, thereby lubricating the contact surface between the cylinder sleeve 20 and the piston sleeve 31, while avoiding the excessive volume of the oil storage tank 313, which leads to flow loss.

[0055] Further, such as Figure 8 As shown, the distance H5 between the oil storage tank 313 and the corresponding limiting channel 311 and the distance H6 between the two limiting channels 311 satisfy the following conditions: 0.1 mm ≤ H5 ≤ H6. Figure 8 For example, the distance H5 between the oil storage tank 313 and the corresponding limiting channel 311 is the distance between the bottom edge of the oil storage tank 313 and the bottom surface of the limiting channel 311. The distance H6 between the two limiting channels 311 is the distance between the bottom surfaces of the two limiting channels 311. Through the above arrangement, it can be ensured that the oil storage tank 313 is not connected to the variable volume chamber 312, and the high-pressure liquid is prevented from leaking directly from the oil storage tank 313 to the variable volume chamber 312, which affects the heat exchange and performance of the pump body assembly.

[0056] It should be noted that the above-mentioned height or length is in the axial direction of the crankshaft 10 .

[0057] Further, such as Figures 7 and 8 , Fig.11 As shown, the width B of the oil storage tank 313 satisfies: 0.5mm≤B≤5mm. The depth H7 of the oil storage tank 313, the diameter D1 of the piston sleeve 31, and the width L2 of the limiting channel 311 satisfy: 0.2mm≤H7≤0.1*(D1-L2). It can be understood that the depth H7 of the oil storage tank 313 is the distance along the radial direction of the piston sleeve 31. The width L2 of the limiting channel 311 is the distance between the two inner sides of the limiting channel 311. Through the above-mentioned settings, it is possible to ensure that the oil storage tank 313 has sufficient oil storage, while avoiding the oil storage tank 313 from being too large in volume, resulting in flow loss.

[0058] In this embodiment, the oil storage tank 313 is a rotary cut trapezoidal groove. It is understandable that the piston sleeve 31 in this embodiment is cylindrical, and the rotary cut trapezoidal groove is formed by the cutting knife rotating and cutting in the vertical direction, so the left and right sides thereof will form arc edges similar to chamfers. The above method is adopted to facilitate the processing of the oil storage tank 313, thereby improving the processing efficiency. Of course, the oil storage tank 313 can also be a sinking straight groove, a trapezoidal groove or a circular sinking groove, which can be selected according to actual needs.

[0059] Further, such as Fig.12 As shown, when the oil storage tank 313 is a rotary cut trapezoidal groove or a trapezoidal groove, the bottom vertex angle β of the oil storage tank 313 satisfies: 95°<β<175°. In other words, the opening angle of the oil storage tank 313 ranges from 5° to 85°. Through the above arrangement, the edge deburring process of the oil storage tank 313 can be reduced, the manufacturing process can be simplified, and leakage caused by excessive opening angle can be prevented.

[0060] In an alternative embodiment, if Figures 4 to 6 , Figures 9 to 11 As shown, the piston sleeve 31 is provided with a central hole 314 for avoiding the crankshaft 10 and an oil hole 315 extending radially, and the oil hole 315 is respectively connected with the central hole 314 and the oil storage tank 313. That is, the oil storage tank 313 and the oil hole 315 in this embodiment are arranged correspondingly.

[0061] Furthermore, the periphery of the oil hole 315 is located within the periphery of the bottom of the oil storage tank 313. Through the above arrangement, the deburring process outside the oil hole 315 can be reduced, simplifying the manufacturing process.

[0062] The present application also provides a fluid machine, comprising the above-mentioned pump body assembly. Specifically, the pump body assembly is a fluorine pump.

[0063] From the above description, it can be seen that the above-mentioned embodiments of the present invention achieve the following technical effects: by adding an oil storage groove 313 on the outer circumferential surface of the piston sleeve 31, the lubrication between the contact surface of the piston sleeve 31 and the cylinder sleeve 20 can be improved, the wear between the inner circle of the cylinder sleeve 20 and the outer circle of the piston sleeve 31 can be reduced, and the friction power consumption is greatly reduced, thereby ensuring the energy efficiency of the pump body assembly, and then improving the operation reliability of the pump body assembly.

[0064] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0065] Unless otherwise specifically stated, the relative arrangement of the parts and steps described in these embodiments, numerical expressions and numerical values ​​do not limit the scope of the present invention. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to the actual proportional relationship. The technology, methods and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be regarded as a part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once a certain item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.

[0066] In the description of the present invention, it is necessary to understand that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the devices or elements referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention. The directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0067] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" may include both "above" and "below". The device may also be positioned in other different ways, rotated 90 degrees or in other orientations, and the spatially relative descriptions used herein are interpreted accordingly.

[0068] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. If not otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0069] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0070] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the numbers used in this way can be interchanged where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein.

[0071] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A pump assembly, characterized in that: include: A crankshaft (10), wherein the crankshaft (10) is provided with two eccentric parts (11) along its axial direction; A cylinder sleeve (20), wherein the crankshaft (10) and the cylinder sleeve (20) are eccentrically arranged with a fixed eccentric distance; A piston assembly (30), the piston assembly (30) comprising a piston sleeve (31) and a piston (32), wherein: The piston sleeve (31) is rotatably arranged in the cylinder sleeve (20), and the piston sleeve (31) has two limiting channels (311). The two limiting channels (311) are arranged in sequence along the axial direction of the crankshaft (10), and the limiting channels (311) extend along the radial direction of the piston sleeve (31). The outer peripheral surface of the piston sleeve (31) is provided with an oil storage groove (313) for storing cooling oil; The piston (32) has a through hole (321), there are two pistons (32), the two eccentric parts (11) extend into the two through holes (321) of the two pistons (32) respectively, the two pistons (32) are slidably arranged in the two limiting channels (311) and respectively form two variable volume chambers (312), the two variable volume chambers (312) are respectively located in the sliding direction of the two pistons (32), the crankshaft (10) rotates to drive the piston (32) to slide back and forth in the limiting channel (311) and interacts with the piston sleeve (31) so that the piston sleeve (31) and the piston (32) rotate in the cylinder sleeve (20); Flanges (40), there are two flanges (40), and the two flanges (40) are respectively arranged at two axial ends of the cylinder sleeve (20); The cylinder sleeve (20) is provided with a liquid inlet channel (21) and a liquid discharge channel (22); the liquid inlet channel (21) is connected to the variable volume chamber (312) and transports refrigerant into the variable volume chamber (312); the liquid discharge channel (22) is connected to the variable volume chamber (312) and discharges the refrigerant in the variable volume chamber (312) through the liquid discharge channel (22).

2. The pump assembly according to claim 1, characterized in that: The cylinder sleeve (20) has a central portion (23), the central portion (23) divides the liquid inlet channel (21) into two sub-channels, the two sub-channels are respectively connected to the two variable volume chambers (312), and the sealing height H1 between the piston sleeve (31) and the central portion (23), the length L1 of the oil storage groove (313), and the height H3 of the central portion (23) satisfy the following relationship: 0.1 mm ≤ H1 ≤ H3 - L1 - 0.1 mm.

3. The pump assembly according to claim 1, characterized in that: The overlapping height H2 between the oil storage groove (313) and the drainage channel (22) and the width H4 of the drainage channel (22) satisfy the following relationship: 0.1 mm ≤ H2 ≤ 0.8 × H4.

4. The pump assembly according to claim 1, characterized in that: The cylinder sleeve (20) has a central portion (23), the central portion (23) divides the liquid inlet channel (21) into two sub-channels, the two sub-channels are respectively connected to the two variable volume chambers (312), and the distance H5 between the oil storage tank (313) and the corresponding limit channel (311) and the distance H6 between the two limit channels (311) satisfy the following conditions: 0.1 mm ≤ H5 ≤ H6.

5. The pump assembly according to claim 1, characterized in that: The width B of the oil storage groove (313) satisfies: 0.5 mm ≤ B ≤ 5 mm.

6. The pump assembly according to claim 1, characterized in that: The depth H7 of the oil storage groove (313), the diameter D1 of the piston sleeve (31), and the width L2 of the limiting channel (311) satisfy the following relationship: 0.2 mm ≤ H7 ≤ 0.1*(D1-L2).

7. The pump assembly according to claim 1, characterized in that: When the oil storage groove (313) is a rotary cut trapezoidal groove or a trapezoidal groove, the bottom vertex angle β of the oil storage groove (313) satisfies: 95°<β<175°.

8. The pump assembly according to claim 1, characterized in that: The oil storage groove (313) is arranged corresponding to the radial opening of the limiting channel (311).

9. The pump assembly according to claim 1, characterized in that: There are one or more oil storage grooves (313). When there are multiple oil storage grooves (313), the multiple oil storage grooves (313) are arranged at intervals along the circumference of the piston sleeve (31).

10. The pump assembly according to claim 1, characterized in that: The piston sleeve (31) is provided with a central hole (314) for avoiding the crankshaft (10) and an oil hole (315) extending in the radial direction, and the oil hole (315) is respectively connected to the central hole (314) and the oil storage tank (313).

11. The pump assembly according to claim 10, characterized in that: The periphery of the oil hole (315) is located within the periphery of the bottom of the oil storage tank (313).

12. The pump assembly according to claim 1, characterized in that: The oil storage groove (313) is any one of a rotary cut trapezoidal groove, a sunken straight groove, a trapezoidal groove or a circular sunken groove.

13. The pump assembly according to claim 1, characterized in that The two eccentric parts (11) are arranged at an angle of 180°.

14. A fluid machine, characterized in that: A pump body assembly comprising any one of claims 1 to 13.

15. The fluid machine according to claim 14, characterized in that: The fluid machinery is a fluorine pump.

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